Inking pump mechanism for printing machines

ABSTRACT

An inking mechanism for supplying ink, by means of a measuring pump, to the ink rail of a printing machine. The pumping mechanism having a piston plunger rotatively and reciprocably carried in a ported cylinder and connected at one end to a crank mechanism for imparting the reciprocal motion. The angle of the crank mechanism and thereby the stroke of the plunger which regulates the amount of ink being supplied, is controlled by an adjusting mechanism which is operated either manually or remotely by means of an indexing motor. The pumping mechanism is driven through shafts and gearing directly from the press drive and may be silenced during nonprinting operations by means of an electrical clutch arrangement.

0 United States Patent 11 1 3,636,873 Fusco 51 Jan. 25, 1972 [54] INKING PUMP MECHANISM FOR 2,450,570 10/1948 Topham 103/157 X N I MACHINES 2,469,796 5/1949 Stobb et al.... 101/207 2,622,523 12/1952 Dressel et al.. 101/366 X [72] Inventor: Ralph L. Fusco, Commack, NY. 2,821,919 2/1958 Dressel ..101/365 [73] Assignee: Wood Industries, Inc., Plainfield, NJ. ggzg [22] Filed: Feb. 27,1969 3,098,437 7/1963 Tyma, Jr. et al. ..101/350 3,168,872 2/1965 Pinkerton ..103/157 [211 APPl- 803,023 3,366,051 1/1968 Fusco ..10l/366 x R l t d .A

e a e U s pphcauon Data Primary Examiner.l. Reed Fisher [63] Continuation-impart of Ser. No. 701,631, Jan. 30, AttorneyPennie, Edmonds, Morton, Taylor and Adams 1968, abandoned, which is a continuation-in-part of Ser. No. 431,130, Feb. 8, 1965, Pat. No. 3,366,051, [57] ABSTRACT 52 U.S. c1 ..l01/366 inking mechani? supplyilg by l a [51] Int. Cl. .1 B41f3l/08 Sunng pump to the mk [all of a pnmmg machine The pump- [58] Field 61 Search ..10l/366, 365, 335; 103/157; mechanism f a naively and 230/137 184/33 rec1procab1y earned 1n a ported cylmder and connected at one end to a crank mechanism for imparting the reciprocal mo- 5 tion. The angle of the crank mechamsm and thereby the 6] References Clted stroke of the plunger which regulates the amount of ink being UNITED STATES PATENTS supplied, is controlled by an adjusting mechanism which is operated either manually or remotely by means of an indexing 1,968,166 7/1934 Phyth1an et al. ..l0 /247 UX motor. The pumping mechanism is driven through h ft and 2,039,992 5/1936 Harold l01/366 gearing directly from the press drive and may be silenced dur- 2392706 1/1946 Taylor et a1 3 -101/365 ing nonprinting operations by means of an electrical clutch ar- 2,430,395 11/1947 Tuve 61 a1. ..103/157 x ,angemem 2,436,492 2/1948 Shepard ..103/157 11 Claims, 7 Drawing Figures PATENTED JANZS 1972 SHEET 1 OF 5 I I V INVE 'roR JANZSIQQ sum u or 5 INVENTOR PATENTEU JANZS m2 SHEET 5 BF 5 INVENTOR @W 9% INKING PUMP MECHANISM FOR PRINTING MACHINES This invention is a continuation-in-part of application Ser. No. 701,631, filed Jan. 30, 1968, now abandoned, which is, in turn, a continuation-in-part of application Ser. No. 431,130, filed Feb. 8, 1965, now U.S. Pat. No. 3,366,051.

BACKGROUND OF THE INVENTION The present application relates to inking mechanisms for printing machines, and more particularly to such mechanisms in which ink is supplied by means of measuring pumps to an ink rail which applies it to the first drum of an ink motion for inking a plate or printing cylinder.

Typical ink-pumping mechanisms of this character as heretofore used are shown, for example, in prior U.S. Pat. Nos. 1,214,856; 1,311,198; 1,589,148, the pumping mechanisms being contained within an ink reservoir equipped with a sliding plate valve mechanism operating in the reservoir, and the rate of ink supply being varied by adjustably limiting the stroke of the pumps. While such pumps have operated very satisfactorily, the valving mechanism is subject to a certain amount of wear and there is a tendency for the rate of pumping to vary objectionably from proportionality to speed of operation of the press. With thicker inks, difficulty may also be encountered due to failure of the pump cylinders to fill completely at each stroke of the pumps. The constructions are also not adapted to remote control in a simple manner, and the location of the pumping mechanism at the end of the ink rail and beyond the frame has required excessively long conduits to more remote nozzles of the ink rail and has required a great variation in the length of the various conduits. The conduits and other elements have also been comparatively inaccessible for inspection and repairs.

A variety of improvements on such pumping mechanisms have been proposed, as, for example, in I-Iuck U.S. Pat. No. 2,695,561, in which the pumping elements have been incorporated in the rail itself and distributed along its length. Such mechanisms have, however, been comparatively complicated and difficult to service and have also presented difficulties in changing from one color of ink to another.

More recently, considerable improvement has been made, as shown in Neal and Pilitz U.S. Pat. No. 3,065,693, by separating the pumping units from the reservoirs, circulating the ink and pressurizing the pump inlets. These constructions are still subject to some of the difficulties above mentioned, and the complication and precision of parts required is to some extent a drawback in pumps of this character.

Previous designs have also been incapable of automatically silencing or deactivating the pumping elements during nonprinting operations of the press, such as the webbing-up operation or the occurrence of a web break, thereby resulting in the heavy buildup and accumulation of ink on the ink train, particularly the lower rollers thereof. This buildup of ink will either by slung off these rollers when the press speed is increased, resulting in contamination of surrounding equipment, or it will find its way up the ink motion flooding the printing plates and eventually causing smears on the travelling web thereby producing waste.

It is the general object of the present invention to provide an improved ink-measuring pump and drive connections therefore, which eliminates the foregoing difficulties.

It is an object of the invention to provide an ink-pumping mechanism without separate valving and in which proportionality of ink delivery to speed of press operation is maintained to the greatest degree possible.

Another object of the invention is to provide an ink-pumping mechanism with remote control for the various pumping elements.

Another object of the invention is to provide an ink-pumping mechanism having an improved and simplified drive mechanism.

Still another object of the invention is to provide an inkpumping mechanism in which the various ink conduits are short and of approximately the same length and in which they are readily accessible for inspection and replacement.

Another object of the invention is to provide an ink-pumping mechanism in which the mechanism may be divided into separable units, as for the various page widths, which can be removed and replaced individually for servicing and repairs.

Another object is to provide an ink-pumping mechanism in which the individual pumps, their drive mechanisms, and their stroke-regulating mechanisms may all be individually inspected and removed and replaced when necessary.

Another object of the invention is to provide a mechanism of the type indicated, in which the individual pumps may be not only remotely adjusted but also adjusted manually.

A further object of the invention is to provide an ink pump having an improved ink distribution.

SUMMARY OF THE INVENTION In the ink-pumping mechanism of the present invention the individual pumping elements comprise piston plungers and ported cylinders, operable without movable valve mechanism, the plungers being driven in convenient groups, as, for example, the eight or nine columns of a page, by a drive mechanism in which the length of stroke of the plunger is adjusted for regulating the ink supply, while leaving the time interval during which the ink is pumped unaffected. Remote and manual adjusting means are provided for each pumping element, and the pumping elements are distributed along the ink rail and connected to the nozzles thereof by comparatively short flexible connections which are accessible for inspection and replacement, while not interfering with the necessary movements of the ink rail. The individual pumping elements are driven from a train of meshing gears, each plunger of a group having one of the gears of the said train mounted thereon. The train of gears is driven from a spur gear mounted on a transverse shaft which in turn is driven through bevel gearing from a main shaft. The main shaft is driven through an electrically operated clutch and other gears directly from the press drive. Thus all the groups of individual pumping elements for the entire printing unit may be easily and automatically silenced when no ink is desired to be fed, as during the webbing-up operation or upon the occurrence of a web break.

An ink-pumping mechanism embodying the invention in a preferred form will now first be described with reference to the accompanying drawing, and the features forming the invention will then be pointed out more particularly in the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS In the drawing:

FIG. I is a somewhat schematic side elevational end view of a unit provided with an inking mechanism of the present invention;

FIG. 2 is an elevational view of the ink-pumping mechanism of the unit of FIG. 1;

FIG. 3 is a plan view of the mechanism of FIG. 2;

FIG. 4 is an elevation view, on an enlarged scale, with parts broken away, of the mechanism shown in FIGS. 1 and 2;

FIG. Sis a section on the line 5-5 of FIG. 3;

FIG. 6 is a plan view of the mechanism of FIG. 4, with parts broken away; and

FIG. 7 is block and schematic diagram of the electrical operation of the clutch.

The inking mechanism of the invention may be applied to printing mechanisms having any of various arrangements of ink motion elements. For definiteness of illustration, it is shown herein, by way of example, as applied to a printing unit of the general type shown in Harless U.S. Pat. No. 2,900,900. The unit is of the familiar arch type, in which the frame 1 accommodates two printing arrangements which may be identical apart from being, respectively, right and left hand. The printing or plate cylinder 2 for one mechanism cooperates with an impression cylinder 3 and is inked by form rollers 4 from an ink drum 5 which is, in turn, inked by a train of transfer rollers 6-7-8 from the initial ink drum 9 which is supplied with ink by an ink rail 10. The ink rail I0 is mounted for pivotal movement about a pivot point llJ-a, so that it may be moved up and down for adjusting its inking position with relation to the first drum 9 of the ink motion or for moving it into and out of operative position. The mounting means for the ink rail form, in themselves, no part of the present invention and may be as shown in the above mentioned Harless patent. The drums 5 and 9 may have an axial reciprocating motion for distributing the ink, as is usual. The ink-pumping mechanism indicated generally at 11 in FIGS. 1 and 2, is supported by a girder element from the frames 1 and runs parallel to and comparatively close to the ink rail 10.

The inking mechanism (FIG. 2) is preferably divided into a number of units A, B, C, D, there being one such unit for each page width of the printing mechanism. Each unit contains a number of measuring pump elements, there being, typically, one such element for each column width of the printing mechanism, and each pumping element communicates through a flexible tubing 12 to the ink rail, for supplying ink to one of the noules thereof.

The units A and C may be right hand, while the units B and D are left hand, so as to simplify the drive connections somewhat as later mentioned. Apart from this, the various units are identical.

The girder element 13 which supports the ink pump units A, B, C, and D is shown in FIGS. 2 and 3. It is generally of an L- section comprising vertical plate 13-0 and horizontal plate l3b. Transverse walls 13-0 support the ink pump units A, B, C, and D, and horizontal transverse elements l3-d provide for mounting the girder to the frame 1, as by means of bolting to brackets or ledges 15, as indicated.

The shafting 16 for driving the pump units is mounted on the vertical girder element 13-11, by means of gear boxes 17 and bearing brackets 18, the drive to the pumping units A, etc., being taken off the shafting 16 by means of bevel gearing and transverse shafts l9. Shafting 16 may be driven through its own motor mechanism 20,- suitably synchronized. with the press operation, or directly from the press drive itself through gear 21. The shafting 16 is segmented by electrical clutch 95, which is of the commercially available type. As seen in FIG. 7, clutch 95 is operated from a power supply through web break detector switch 96, press drive speed switch 97 and a unit selector switch 98, all connected in series with the clutch. If a particular unit is not to be used during a particular run, switch 98 will remain open and no power will be available for operation of the clutch 95 resulting in nonoperation of the pumping units of the nonselected printing unit.

The press drive speed switch 97 is mounted on the drive of the printing press unit and when the press unit is operating at speeds below 100 ft. per minute or when the press is at a standstill the switch contacts are open. The contacts of the switch close when the printing press is accelerated and exceeds the slow starting speed at I00 feet per minute. Consequently no power will be available to operate the clutch 95 when the switch contacts are open. With the clutch deactivated, drive shaft 16 will not rotate and all the pumping units of the printing mechanism will be silenced so that no ink will be delivered to any portion of the ink motion of that printing unit. This means that during the webbing-up of the press, an operation which is conducted at speeds well below 100 ft. per minute, no ink will be pumped onto the ink motion resulting in the elimination of smearing the paper web at the beginning of the run and in the elimination of ink-laden rollers and associated parts of the printing machine, which heretofore was a major contributing factor in undesirable ink sling and ink misting. With the press drive speed switch 97 open, the pumps will not be operating, the rollers and cylinders will be clean (ink-free) during the webbing operation and there will be no ink sling and very little if any of ink misting when the press is brought up to speed. As a result any ink mist suppression system which may be attached to the unit will be able to operate more efficiently with less frequent cleaning of its parts because the amount of contamination build up on its operating surfaces, which directly affect its operating efiiciency, will be greatly reduced.

When the press is brought up to operating speeds, switch 97 will close and the circuit will be closed so that clutch is activated and shaft 16 will be rotated to drive the pumping units.

Web break detector switch 96 is in the closed position when the web is properly threaded through the printing unit, each unit being supplied with such a switch. When a web break occurs in any unit its switch 96 will open, again opening the circuit between clutch 95 and its power supply, resulting in instantaneous shutoff of the pumping units. If the pumps were not shut off, as heretofore was the case, the pumps, operating at the high synchronous speed of the press, would continue to pump ink onto the ink motion, but the ink which is ultimately delivered to the printing cylinder 2 would not be carried away by a web travelling in the printing couple between printing cylinder 2 and impression cylinder 3 resulting in a flooding condition and all the disadvantageous appurtenant thereto. However, with the present mechanism it is possible to avoid this situation by silencing the drive mechanism for the pumping units of the printing mechanism in which the web has broken, by disconnecting the source of power to clutch 95 due to the opening of switch 96.

The pumping unit mechanisms are shown in detail in FIGS. 4 and 5. Each one comprises an upper section or subunit, carried in a housing and frame structure 25, and which contains the pumping elements and their drive, together with a lower section or subunit, carried in a frame structure 26, and which contains the pump adjusting mechanism. A bar or plate 27, supported at its ends in the walls l3-c (FIG. 2) supports the frame elements 26 of the lower subunits and carries the means for operatively connecting the upper and lower subunits together.

The construction and operation of the upper subunit, which contains the pumping mechanism, will now be considered in detail, the lower subunit being described later.

The housing 25 forms a space 28 which contains the pump plunger drive mechanisms, together with oil at a convenient level for lubricating the parts. Bores 29 in the sidewall 30 of member 25 receive the pump cylinder sleeves 31, which have an inktight fit to the bores and are held in place by flanges 32 and screws 33, securing the same to the housing wall 30.

Cylinder sleeve 31 is closed off at its outer end by a screwplug 34 and is cross bored to form an intake port 35 and outlet port 36. The outlet port 36 communicates with a tapped bore 37 to which the flexible connection 12 (FIG. 2) attaches for connecting to the ink rail. The intake port 35 communicates with a bore 38 and thus with channel 39 of a manifold block 40 which fits into and is brazed or otherwise sealed to the wall 30, as shown. Tapped bore 41' takes the hose connec tion 41 for supplying ink to the channel 39.

The piston plunger 42 is rotatively and reciprocably carried in the cylinder bore 43 of the sleeve 31, and is driven by means of a spur gear 44 which is secured to the plunger 42, as by press-fitting. The gears 44 of adjacent plungers mesh with each other, and the gear at one end of the line is driven by a spur gear 45, carried on a drive shaft element 19 (FIG. 3). Each plunger 42 is also provided with a crossarrn 46, which fits in a bore near the plunger end and is held in place by a setscrew 47, for the purpose of imparting a suitable reciprocation to the plunger, as it rotates.

The outer end of arm 46 carries a bearing ball 48 which fits in the socket 49 of a slidable block carried in a radial guideway 50 in a crank member 51 which is rotatably mounted, by means of its shaft 52 and antifriction bearings 53 in a yoke 54. Yoke 54 is mounted for rotary or angular adj ustment about the axis of a pair of trunnions 55, 56. The upper trunnion 55 is rotatable in bar 57 and held in place vertically by snap ring 58. The lower trunnion 56 is fixed to the yoke 54 and rotatably mounted in the bottom of housing 25 for angular adjustment, as below described.

in FIGS. 46, the plunger 42 is shown in the midposition of its stroke, and the yoke 54 in a neutral or nonpumping position, in which the axis of shaft 52 is parallel to the cylinder bore, so that plunger arm 46 merely rotates in a plane at right angles to the plunger axis. In the actual construction chosen for purposes of illustration herein, the cylinder (and plunger) diameter and the plunger maximum stroke are equal, so that the plunger moves to the right and left of the position of FIG. 5 by a distance equal to about half the plunger diameter. in a typical construction, the plunger diameter and total stroke may be three-eighths inch, with other dimensions in proportion. An angular adjustment of yoke 54 of about will produce the required maximum plunger reciprocation, while adjustments to lesser angles will vary the stroke and, hence, pumping rate, as desired.

The plunger 42 is formed with a cutout portion 59 by means of which communication is alternately established between the inlet port 35 and cylinder space 60 and between outlet port 36 and cylinder space 60, Conveniently, the cutout 59 may be formed by a simple flat and the port openings 35, 36 may be circular bores, the port opening being substantially proportional to the sine of the angle of rotation of the plunger. The pumping action is extremely simple: starting in the midposition (FIG. 5), 90 rotation of gear 44 and plunger 42 will complete the suction stroke and also bring the flat 59 to a position where both ports 35 and 36 are blocked off; the next 90 of rotation will bring the flat over the outlet port and discharge ink therethrough, until we again have the position of FIG. 5 but with the flat 59 at the top, instead of the bottom, of the plunger; a third 90 of rotation completes the discharge stroke and brings the flat to a position where both ports are blocked off; while the fourth and last 90 accomplishes the first half of the suction stroke and brings the parts again to the position of FIG. 5.

The plungers 42, with their gears 44 and crossarms 46, may

all be the same, and may be set in different angular positions in assembling the unit. Thus, with eight plungers in the unit, using gears 44 with 24 teeth permits setting each plunger ahead of the preceding by three teeth (45), so that the eight plungers are operating at any given time in eight different phase positions, and the power consumption is practically steady.

The speed of operation of the mechanism is sufficiently low so that the forces due to mass accelerations may be neglected. Under normal operating conditions, the discharge pressure of the ink is moderate, in a range such as 10 to pounds per square inch. With a plunger of three-eighths inch diameter, the cylinder area is only about onetenth square inch, and the hydraulic pressure force on the plunger is between i and 2 pounds.

Each plunger 42 is selectively fitted to its cylinder sleeve bore 43 and is otherwise unconstrained in its movements. The gears 44 are preferably involute, being capable of meshing with true gear action of slightly difierent center distances, do not subject the plunger to any further requirement of alignment, other than that imposed by the cylinder bores 43. The forces on each gear consist of a tooth pressure on the driven side of the gear and a somewhat less tooth pressure on the driving side of the gear, which forces resolve into a fluctuating couple and small resultant lateral force. The length of plunger 42 within the cylinder bore 43 is sufficient to maintain alignment, without any tendency toward scuffing action, and with a factor of safety, far in excess of the lateral forces produced by the gearing 44 and idle crank drive 46-51. It will be noted that small displacements of the yoke 54 and of the crank mechanism carried thereby will not appreciably affect the action of the pump. It is, therefore, possible in the pump construction of the present invention, to fit the plunger and cylinder sleeve selectively and to permit interchange and replacement of the parts without requiring high precision in the remainder of the mechanism.

The adjusting mechanism for the stroke of plungers 42 comprises, for each plunger, a coupling member 65 secured to trunnion 56 and interfitting with coupling member 66 carried on the plate 27 and rotatably mounted therein by shaft section 67, the lower end of which carries a slotted arm 68 receiving a slidable bushing member 69 which holds a crankpin 70. Crankpin 70, the axis of which is spaced from the axis of shaft section 67, fits into a cross slot 71 formed in the top ofa nut 72 which fits on the threaded section 73 of shaft 74, being moved axially of the shaft 74 as the latter is rotated and thus accomplishing the adjusting movement for controlling the reciprocation of plunger 42, by adjusting the angle of the idler crank mechanism carried in the yoke 54 between parallelism (actually, substantial coincidence) to the plunger axis 42 and about l5 inclination with respect to the said axis, so as to adjust between zero and full stroke of the plunger.

The shaft 74 is fixed to and carried by an inner shaft element 75 journaled in the plates 26 and having an extension 76 at one end. Extension 76 has a square end 77 and may be used for manual adjustment of the stroke of plunger 42. Shaft 74 carries a gear 78 meshing with and driven by pinion 79 which is carried on and driven by the shaft 80 of indexing motor 81. Indexing motor 81 is of the known commercially available type utilizing a permanent magnet rotor, for moving in substantially a uniform increment upon each actuation and permitting stalling or overpowering by the manual adjustment. Shaft 74 carries a second gear 82 meshing with gear wheel 83 rotatably mounted on a sideplate 26 by the bolt and shaft arrangement 84. Gear wheel 83 has a slot 85 accommodating the stop pin 86 for limiting the rotary movement of wheel 83 and, hence, of shaft 74 and thus setting the stroke adjustment range for the plunger 42.

The arrangement of the adjustment mechanism is the same for all plungers, with the exception that the motors 81' for alternating plungers are positioned oppositely to the motors 81, so as to economize space, the shaft 74, gears carried thereby and meshing gears also being reversed. inasmuch as each plunger and cylinder has not only its own manual adjustment, but also its own motor adjustment by means of motor 81 or 81, the entire inking arrangement may be controlled page by page and column by column from a control panel at each unit and also by a master control panel at the folder or other desired location.

What is claimed is:

1. An inking mechanism for supplying ink to the ink rail of a printing machine ink motion, comprising the combination of a housing accommodating a plurality of measuring pump elements, each having a cylinder bore with a discharge port and intake port in its wall, a plunger rotatably and reciprocably carried in the bore, said plunger having a recess in one side for communicating alternately with the intake and discharge port, means for supplying ink to the intake ports and means for connecting the discharges of said elements to the ink rail at spaced points therealong for supplying ink thereto, means for reciprocating the plungers, comprising, for each plunger an idle crank mechanism operable to reciprocate the plunger as it rotates comprising a yoke mounted on said housing for angular rotation, a crank member rotatably mounted in said yoke and a crossarm having one end thereof secured to said crank member by means of a ball joint and the other end thereof secured to said plunger, means for angularly adjusting the said crank mechanism for varying the stroke of the plunger and rate of pumping, drive means for the said pump elements comprising a train of meshing gears rotatively fixed to the said plungers for rotating the said plungers and axially moveable therewith, a transverse shaft mounted in said housing for each of said plurality of measuring pump elements for driving'said train of meshing gears, a drive shaft mounted adjacent said housing for driving said transverse shafts through bevel gears, gear and shaft means connecting said drive shaft to the main press drive of the printing machine so that said pump elements are driven at a synchronous speed therewith, electrical clutch means connecting said drive shaft to said gear and shaft means, a source of electrical power for operating said clutch means, and a plurality of separately operable electrical switch means connected in series between said clutch and said power source for opening the electrical circuit between said power source and said clutch and for independently and automatically deactivating said clutch and silencing said main drive shaft and said pumping elements upon either the occurrence of a web break or at web-threading speeds or press speeds otherwise below normal running speed, said electrical switch means being connected between said clutch means and its source of electrical power for also automatically activating said clutch means when both web is being fed through the press and the press is running at normal running speed above web threading speed.

2. The inking mechanism according to claim 1 wherein said switch means for automatically opening said circuit between said clutch and its power source at press speeds below normal running speeds comprises a press drive speed responsive switch mounted on the main drive of said printing machine having its contacts closed only at normal running speeds of said machine so that no power will be transmitted to said electrical clutch at speeds below normal running speeds thereby preventing rotation of said main drive shaft so that no ink is being pumped by said pumps.

3. The inking mechanism according to claim 2 wherein said running speed is 100 feet per minute.

4. The inking mechanism according to claim 1 in which the said means for adjusting the crank mechanism comprises a step-by-step electric motor for each measuring pump element, means operable thereby for angularly adjusting the said crank mechanism.

5. The inking mechanism according to claim 4 comprising also manual adjustment means for the said crank mechanism.

6. The inking mechanism according to claim 5 comprising a screwand nut connection, the screw being rotatively adjustable by the said motor and manual means and the nut being coupled to the said crank mechanism for adjusting the same by means of interfitting coupling members.

7. The inking mechanism according to claim 1 wherein said switch means for automatically opening said circuit between said clutch and its power source upon occurrence of a web break comprises a web break detector switch mounted on the printing machine having its contacts closed when said web is threaded through said printing machine and is unbroken, whereby said web break detector switch is opened upon the occurrence of a web break so that no power will be transmitted to said electric clutch thereby preventing rotation of said main drive shaft so that no ink is being pumped by said pumps.

8. The inking mechanism according to claim 7 wherein said switch means for automatically opening said circuit between said clutch and its power source at press speeds below normal running speeds further comprises a press drive speed switch mounted on the main drive of said printing machine having its contacts closed only normal running speeds of said machine so that no power will be transmitted to said electrical clutch at speeds below normal running 9. The inking mechanism according to claim 7 in which the said means for adjusting the crank mechanism comprises a step-by-step electric motor for each measuring pump element, means operable thereby for angularly adjusting the said crank mechanism.

10. The inking mechanism according to claim 9 comprising also manual adjustment means for the said crank mechanism.

11. The inking mechanism according to claim 10 comprising a screw and nut connection, the screw being rotatively adjustable by the said motor and manual means and the nut being coupled to the said crank mechanism for adjusting the same by means of interiitting coupling members. 

1. An inking mechanism for supplying ink to the ink rail of a printing machine ink motion, comprising the combination of a housing accommodating a plurality of measuring pump elements, each having a cylinder bore with a discharge port and intake port in its wall, a plunger rotatably and reciprocably carried in the bore, said plunger having a recess in one side for communicating alternately with the intake and discharge port, means for supplying ink to the intake ports and means for connecting the discharges of said elements to the ink rail at spaced points therealong for supplying ink thereto, means for reciprocating the plungers, comprising, for each plunger an idle crank mechanism operable to reciprocate the plunger as it rotates comprising a yoke mounted on said housing for angular rotation, a crank member rotatably mounted in said yoke and a crossarm having one end thereof secured to said crank member by means of a ball joint and the other end thereof secured to said plunger, means for angularly adjusting the said crank mechanism for varying the stroke of the plunger and rate of pumping, drive means for the said pump elements comprising a train of meshing gears rotatively fixed to the said plungers for rotating the said plungers and axially moveable therewith, a transverse shaft mounted in said housing for each of said plurality of measuring pump elements for driving said train of meshing gears, a drive shaft mounted adjacent said housing for driving said transverse shafts through bevel gears, gear and shaft means connecting said drive shaft to the main press drive of the printing machine so that said pump elements are driven at a synchronous speed therewith, electrical clutch means connecting said drive shaft to said gear and shaft means, a source of electrical power for operating said clutch means, and a plurality of separately operable electrical switch means connected in series between said clutch and said power source for opening the electrical circuit between said power source and said clutch and for independently and automatically deactivating said clutch and silencing said main drive shaft and said pumping elements upon either the occurrence of a web break or at web-threading speeds or press speeds otherwise below normal running speed, said electrical switch means being connected between said clutch means and its source of electrical power for also automatically activating said clutch means when both web is being fed through the press and the press is running at normal running speed above web threading speed.
 2. The inking mechanism according to claim 1 wherein said switch means for automatically opening said circuit between said clutch and its power source at press speeds below normal running speeds comprises a press drive speed responsive switch mounted on the main drive of said printing machine having its contacts closed only at normal running speeds of said machine so that No power will be transmitted to said electrical clutch at speeds below normal running speeds thereby preventing rotation of said main drive shaft so that no ink is being pumped by said pumps.
 3. The inking mechanism according to claim 2 wherein said running speed is 100 feet per minute.
 4. The inking mechanism according to claim 1 in which the said means for adjusting the crank mechanism comprises a step-by-step electric motor for each measuring pump element, means operable thereby for angularly adjusting the said crank mechanism.
 5. The inking mechanism according to claim 4 comprising also manual adjustment means for the said crank mechanism.
 6. The inking mechanism according to claim 5 comprising a screw and nut connection, the screw being rotatively adjustable by the said motor and manual means and the nut being coupled to the said crank mechanism for adjusting the same by means of interfitting coupling members.
 7. The inking mechanism according to claim 1 wherein said switch means for automatically opening said circuit between said clutch and its power source upon occurrence of a web break comprises a web break detector switch mounted on the printing machine having its contacts closed when said web is threaded through said printing machine and is unbroken, whereby said web break detector switch is opened upon the occurrence of a web break so that no power will be transmitted to said electric clutch thereby preventing rotation of said main drive shaft so that no ink is being pumped by said pumps.
 8. The inking mechanism according to claim 7 wherein said switch means for automatically opening said circuit between said clutch and its power source at press speeds below normal running speeds further comprises a press drive speed switch mounted on the main drive of said printing machine having its contacts closed only normal running speeds of said machine so that no power will be transmitted to said electrical clutch at speeds below normal running
 9. The inking mechanism according to claim 7 in which the said means for adjusting the crank mechanism comprises a step-by-step electric motor for each measuring pump element, means operable thereby for angularly adjusting the said crank mechanism.
 10. The inking mechanism according to claim 9 comprising also manual adjustment means for the said crank mechanism.
 11. The inking mechanism according to claim 10 comprising a screw and nut connection, the screw being rotatively adjustable by the said motor and manual means and the nut being coupled to the said crank mechanism for adjusting the same by means of interfitting coupling members. 